CN101513834B - Multi-speed transaxle for a front wheel drive vehicle - Google Patents
Multi-speed transaxle for a front wheel drive vehicle Download PDFInfo
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- CN101513834B CN101513834B CN2009100080679A CN200910008067A CN101513834B CN 101513834 B CN101513834 B CN 101513834B CN 2009100080679 A CN2009100080679 A CN 2009100080679A CN 200910008067 A CN200910008067 A CN 200910008067A CN 101513834 B CN101513834 B CN 101513834B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A front wheel drive transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes a sun gear member, a planet carrier member, and a ring gear member. The torque transmitting devices include clutches and brakes arranged within a transmission housing.
Description
The cross reference of related patent U.S. Patent No.
The application requires to enjoy in the U.S. Provisional Application No.61/030 that submitted on February 21st, 2008,261 rights and interests, and it combines in this article by reference and intactly.
Technical field
The present invention relates generally to a kind of multi-step transmissions with a plurality of compound planet gears and a plurality of torque transmitters, has the eight kinds of speed or the change-speed box of multiple speed, four compound planet gears and a plurality of torque transmitters more more specifically to a kind of for what f-w-d vehicle disposed.
Background technology
Statement in this section only provides the background information that openly is associated with the present invention, and can form or not form current techniques.
The representative type multi-step transmissions uses a plurality of torque-transmitting mechanisms, planetary wheel to arrange the combination of (planetary gear arrangements) and the interconnecting member of fixing, to obtain a plurality of gear ratios.The quantity of compound planet gear and physical arrangement are recently confirmed by encapsulation technology, cost and required speed usually.
Though current change-speed box has been realized its its intended purposes; But the demand for new improved transmission configuration is that basic continuing exists; It has embodied especially considers improved performance from efficient, responsibility and flatness, and improved encapsulation, mainly is size and the weight that reduces.Therefore, need a kind of improved, possess cost-efficient, compact multi-step transmissions.
Summary of the invention
In one aspect of the invention, a kind of transaxle (transaxle) is provided, it has gear box input parts, gearbox output parts, a plurality of compound planet gear and a plurality of torque-transmitting mechanisms.
In another aspect of this invention, a kind of shell with first wall, second wall and the 3rd wall is provided, said the 3rd wall extends between the first wall and second wall.In shell, be provided with first compound planet gear, second compound planet gear, the third line star gear cluster and fourth line star gear cluster.First compound planet gear is adjacent to first wall, and second compound planet gear is adjacent to second wall, and fourth line star gear cluster is adjacent to first compound planet gear, and the third line star gear cluster is between the fourth line star gear cluster and second compound planet gear.
In another aspect of this invention, each compound planet gear has sun gear parts, ring gear component and planet carrier parts, and it supports a plurality of planetary wheels, and each planetary wheel is configured to be meshing with each other with sun gear parts and ring gear component.The ring gear component of first compound planet gear for good and all is connected on the sun gear parts of second compound planet gear; The sun gear parts of first compound planet gear for good and all are connected on the sun gear parts of fourth line star gear cluster, and the ring gear component of the third line star gear cluster for good and all is connected on the planet carrier parts of fourth line star gear cluster.
In still another aspect of the invention, output block for good and all links with the carriage member of second compound planet gear and the third line star gear cluster.Input block for good and all links with the carriage member of first compound planet gear.
In still another aspect of the invention, shell has to be defined as from the neighboring of compound planet gear and radially inwardly and axially goes up the first area of being defined (bounded) by the first wall and first compound planet gear.Second area is defined as from the neighboring of compound planet gear and radially inwardly and is axially upward defined by first compound planet gear and fourth line star gear cluster.The 3rd area limiting is defined by fourth line star gear cluster and the third line star gear cluster for radially inwardly and axially going up from the neighboring of compound planet gear.The 4th area limiting is defined by second compound planet gear and the third line star gear cluster for radially inwardly and axially going up from the neighboring of compound planet gear.The 5th area limiting is defined by second compound planet gear and second wall for radially inwardly and axially going up from the neighboring of compound planet gear.The 6th area limiting is radially inside and radially outside from the neighboring of compound planet gear from the 3rd wall, and axially goes up and defined by the first wall and second wall.
In still another aspect of the invention; First clutch is arranged in wherein at least one zone in first area, second area, the 3rd zone and the 6th zone; And can engage selectively, so that the ring gear component of first compound planet gear and the sun gear component interconnect of the third line star gear cluster are got up.
In still another aspect of the invention; Second clutch is arranged in wherein at least one zone in first area, second area, the 3rd zone and the 6th zone; And can engage selectively, so that the planet carrier parts of first compound planet gear and the sun gear component interconnect of the third line star gear cluster are got up.
In still another aspect of the invention; Three-clutch is arranged in wherein at least one zone in the 4th zone, the 5th zone and the 6th zone; And can engage selectively, so that the ring gear component of second compound planet gear and the sun gear component interconnect of the third line star gear cluster are got up.
In still another aspect of the invention; First drg is arranged in wherein at least one zone in first area, second area, the 5th zone and the 6th zone; And can engage selectively, so as with the sun gear component interconnect of the sun gear parts of first compound planet gear and fourth line star gear cluster to shell.
In still another aspect of the invention, second drg is arranged in wherein at least one zone in first area, second area, the 5th zone and the 6th zone, and can engage selectively, so that the ring gear component of fourth line star gear cluster is interconnected on the shell.
In still another aspect of the invention, power-transfer clutch and drg can engage selectively, so that between gear box input parts and gearbox output parts, set up at least eight speed of advances ratios and at least one reverse speed ratio.
In still another aspect of the invention, a kind of power transfer assemblies (power transfer assembly) has first transmission gear (transfer gear) and second transmission gear and power transmission component.First transmission gear rotatably is fixed on the driving engine output block, and second transmission gear rotatably is fixed on the gear box input parts.Power transmission component rotatably is connected on first transmission gear and second transmission gear, is used for rotation energy is sent to second transmission gear from first transmission gear.
In still another aspect of the invention; The main reduction gear compound planet gear has the main reduction gear sun gear that is connected on the gearbox output parts, is connected in main reduction gear Ring gear and main reduction gear carriage member on the transmission case; It is rotatably supporting a plurality of miniature gearss of main reduction gear, and a plurality of miniature gearss of main reduction gear and main reduction gear sun gear and main reduction gear Ring gear all are meshing with each other.
In still another aspect of the invention, differential gear set has the differential gear box that is connected on the main reduction gear carriage member, and has a pair of gear that rotatably is supported in the differential gear box.This rotatably is fixed on one of them of pair of wheels (road wheels) one of them of gear, and this rotatably is fixed on this in the wheel another in the gear another.
From the specification sheets that this paper provides with further distinct suitable application area.Should understand that specification sheets and specific example are only only presented for purposes of illustration, and are not intended to limit scope disclosed by the invention.
Description of drawings
Drawing described here is just from illustrational purpose, and intention limits scope disclosed by the invention by no means.
Figure 1A is the scheme drawing that is used for the arrangement of gears of front wheel drive transmission in accordance with the principles of the present invention;
Figure 1B has shown the chart according to the position of the torque transmitter of the compound planet gear that is used to be provided with the change-speed box shown in Figure 1A of the embodiment of the invention; With
Fig. 2 is the front wheel drive type transaxle schematic representation of apparatus of arrangement of gears that comprises the change-speed box of Figure 1A and Figure 1B in accordance with the principles of the present invention.
The specific embodiment
Below being described in only is exemplary in nature, and be not intended to limit that the present invention is open, application or purposes.
Referring now to Figure 1A,, label 10 is generally represented an embodiment of front wheel drive type multi-step transmissions or eight speed automatic transmission.Shown in change-speed box 10 be front wheel drive transmission or lateral velocity variation device, but can adopt the change-speed box configuration of various other types.Change-speed box 10 comprises transmission case 12, input shaft or input block 14, output shaft or output block 16 and arrangement of gears 18.Input block 14 is connected on the driving engine (shown in Fig. 2) constantly, or is connected on the turbine (not shown) of torque converter.Output block 16 links to each other with main reduction gear unit (not shown) or auxiliary gear box (shown in Fig. 2) constantly.
The arrangement of gears 18 of change-speed box 10 comprises first compound planet gear 20, second compound planet gear 22, the third line star gear cluster 24 and fourth line star gear cluster 26.Compound planet gear 20,22,24 and 26 are connected between input block 14 and the output block 16.
In a preferred embodiment of the invention; Compound planet gear 20 comprises ring gear component 20A, planet carrier parts 20B and sun gear parts 20C, and planet carrier parts 20B is rotatably supporting one group of planetary wheel or miniature gears 20D (only having shown one of them among the figure).Ring gear component 20A and primary shaft or first centre part 42 and second or second centre part 44 are connected, so that common rotation.Planet carrier parts 20B and input shaft or input block 14 and third axle or the 3rd centre part 46 are connected, so that common rotation.Sun gear parts 20C is connected with the 4th or the 4th centre part 48, so that common rotation.Miniature gears 20D respectively is configured to be meshing with each other with sun gear parts 20C and ring gear component 20A.
Compound planet gear 22 comprises ring gear component 22A, planet carrier parts 22B and sun gear parts 22C, and planet carrier parts 22B is rotatably supporting one group of planetary wheel or miniature gears 22D.Ring gear component 22A is connected with the 5th or the 5th centre part 50, so that common rotation.Planet carrier parts 22B is connected with output shaft or output block 16, so that common rotation.Sun gear parts 22C is connected with second or second centre part 44, so that common rotation.Miniature gears 22D respectively is configured to be meshing with each other with sun gear parts 22C and ring gear component 22A.
Compound planet gear 24 comprises ring gear component 24A, planet carrier parts 24B and sun gear parts 24C, and planet carrier parts 24B is rotatably supporting one group of planetary wheel or miniature gears 24D.Ring gear component 24A is connected with the 6th or the 6th centre part 52, so that common rotation.Planet carrier parts 24B is connected with output shaft or output block 16, so that common rotation.Sun gear parts 24C and the 7th or the 7th centre part 54 and the 8th or the 8th centre part 56 are connected, so that common rotation.Miniature gears 24D respectively is configured to be meshing with each other with sun gear parts 24C and ring gear component 24A.
Compound planet gear 26 comprises ring gear component 26A, carriage member 26B and sun gear parts 26C, and planet carrier parts 26B is rotatably supporting one group of planetary wheel or miniature gears 26D.Ring gear component 26A is connected with the 9th or the 9th centre part 58, so that common rotation.Planet carrier parts 26B is connected with the 6th or the 6th centre part 52, so that common rotation.Sun gear parts 26C is connected with the 4th or the 4th centre part 48, so that common rotation.Miniature gears 26D respectively is configured to be meshing with each other with sun gear parts 26C and ring gear component 26A.
Change-speed box 10 also comprises a plurality of torque-transmitting mechanisms or torque transmitter, and it comprises first clutch 66, second clutch 68, three-clutch 70, first drg 72 and second drg 74.First clutch 66 can engage selectively, so that primary shaft or first centre part 42 are connected on the 8th or the 8th centre part 56.Second clutch 68 can engage selectively, so that third axle or the 3rd centre part 46 are connected on the 8th or the 8th centre part 56.Three-clutch 70 can engage selectively, so that the 5th parts or the 5th centre part 50 are connected on the 7th or the 7th centre part 54.First drg 72 can engage selectively, so that the 4th or the 4th centre part 48 are connected on the transmission case 12, thereby limiting part 48 is with respect to the rotation of transmission case 12.At last, second drg 74 can engage selectively, so that the 9th or the 9th centre part 58 are connected on the transmission case 12, thereby limiting part 58 is with respect to the rotation of transmission case 12.
Change-speed box 10 can be with at least eight advance torque ratio and reverse gear torque ratios and moment of torsion is passed on output shaft or the output block 16 from input shaft or input block 14.Joint through wherein one or more torque-transmitting mechanisms (being first clutch 66, second clutch 68, three-clutch 70, first drg 72 and second drg 74) obtains each advance torque ratio and reverse gear torque ratio.Those of skill in the art should understand different speed than being associated with each torque ratio.Thereby change-speed box 10 can obtain eight speed of advance ratios.
Shown in Figure 1A; District A is limited in such zone or space; It is by first wall 102, compound planet gear 20, radially inwardly by datum line " L " and radially outward defined by datum line " M ", and datum line " L " is the vertical line of aiming at input shaft 14 vertically, and datum line " M " is to adjoin compound planet gear 20; 22,24 and 26 external diameter or neighboring and the vertical line that extends.Though datum line " M " all is being shown as straight line among these several figure; But should understand datum line " M " be along compound planet gear 20,22,24 and 26 neighboring; And can be stair-stepping or nonlinear therefore; This depends on the position of the neighboring of each compound planet gear 20,22,24 and 26.District B is limited in such zone, and this zone is defined by datum line " L " by datum line " M " and radially inner side by compound planet gear 20, compound planet gear 26, radial outside.District C is limited in such zone, and this zone is defined by datum line " L " by datum line " M " and radially inner side by compound planet gear 24, compound planet gear 26, radial outside.District D is limited in such zone, and this zone is defined by datum line " L " by datum line " M " and radially inner side by compound planet gear 22, compound planet gear 24, radial outside.District E is limited in such zone, and this zone is defined by datum line " L " by datum line " M " and radially inner side by compound planet gear 22, second end wall 104, radial outside.District F is limited in such zone, and this zone is defined by the 3rd wall 106 by datum line " M " and radial outside by first wall 102, second wall 104, radially inner side.
In the arrangement of gears 18 of the change-speed box shown in Figure 1A 10; Compound planet gear 20 is set near first wall 102; Compound planet gear 22 is set near second wall 104; Compound planet gear 26 is set to adjacent to compound planet gear 20, and compound planet gear 24 is arranged between compound planet gear 22 and 26.Torque-transmitting mechanisms is positioned in the specific zone wittingly, so that aspect whole transmission dimensions, packaging efficiency and the minimizing manufacturing complexity advantage is being provided.In the special example shown in Figure 1A, first clutch 66 is arranged among the district A with second clutch 68, and first drg 72 and second drg 74 are arranged among the district F, and three-clutch 70 is arranged among the district D.
Yet the present invention can imagine torque-transmitting mechanisms 66,68, and 70,72 and 74 are arranged on other embodiment in other district.In the chart of Figure 1B, shown torque-transmitting mechanisms 66,68,70,72 and 74 feasible location in these zones.The chart of Figure 1B has been listed power-transfer clutch and drg in Far Left row, and ranks have gone out the district of available positioning clutch/drg on the top." X " expression the present invention imagination in the chart is positioned at power-transfer clutch or drg in the zone listed in the row of top.For example, first drg 72 can be positioned on district A, B, and among E or the F, second drg 74 can be positioned on district A; B, among E or the F, first clutch 66 can be positioned on district A, and B is among C or the F; Second clutch 68 can be positioned on district A, B, and among C or the F, and three-clutch 70 can be positioned on region D, among E or the F.
Referring now to Fig. 2,, shown the f-w-d dynamical system 150 that comprises transaxle 154 according to the embodiment of the invention.Transaxle 154 comprises change-speed box 10, and it has the arrangement of gears 18 of Figure 1A and 1B.Transaxle 154 is installed on the driving engine 156.Like the following stated, driving engine 156 produces driving torque in engine output shaft 157, the input shaft 14 of its drive speed transmission 10.Driving engine 156 is combustion engine normally, yet the present invention can imagine the driving engine of other type, for example genemotor and hybrid power engine.In addition; Transaxle 154 comprises messenger chain or driving band 158, drive sprocket or gear 160, driven sprocket or gear 162, diff 164, main reduction gear compound planet gear 166 and a pair of axle drive shaft 168 and 170, and it drives pair of wheels 172 and 174 respectively.
Messenger chain or driving band 158 engage with drive sprocket or gear 160 at first end 180, and engage with driven sprocket or gear 162 at second end 182.Drive sprocket or gear 160 are connected on engine output shaft or the parts 157.Driven sprocket 162 rotatably is fixed on axle drive shaft or the rotatable parts 159.Axle drive shaft or rotatable parts 159 are connected on the input shaft 14 of change-speed box 10.The output shaft 16 of change-speed box 10 is connected on the output sleeve 163.Output sleeve 163 is connected on the sun gear of main reduction gear compound planet gear 166, to obtain required gear ratio.The carriage member of main reduction gear compound planet gear 166 is supporting a plurality of miniature gearss, and these miniature gearss are meshed with the sun gear and the Ring gear of main reduction gear compound planet gear 166.The carriage member of main reduction gear compound planet gear 166 rotatably is connected on the shell of diff 164, and driving torque is passed to the shell of diff 164.Diff 164 is supported on the bevel gear in the differential gear box rotatably through two groups and sends the driving torque that driving engine 156 is produced to two axle drive shafts 168 and 170. Axle drive shaft 168 and 170 rotatably is fixed on the bevel gear of diff 164, and can be driven by bevel gear independently, thereby with driving torque supply vehicle wheel 172 and 174.
Description of the invention only is exemplary in nature, thereby the modification that does not break away from main points of the present invention will be in the scope of the present invention.This modification is not considered to break away from the spirit and scope of the present invention.
Claims (22)
1. transaxle that is connected on the driving engine output block, said transaxle comprises:
The gear box input parts;
The gearbox output parts;
Transmission case, the 3rd wall that it has first wall, second wall and between said first wall and said second wall, extends;
Be arranged on first compound planet gear, second compound planet gear, the third line star gear cluster and fourth line star gear cluster in the said transmission case; Wherein, Said first compound planet gear is adjacent to said first wall; Said second compound planet gear is adjacent to second wall; Said fourth line star gear cluster is adjacent to said first compound planet gear; And said the third line star gear cluster is between said fourth line star gear cluster and said second compound planet gear, and each said compound planet gear has sun gear parts, ring gear component and supports a plurality of planetary planet carrier parts, and said a plurality of planetary wheels respectively are configured to be meshing with each other with said sun gear parts and said ring gear component; And; Wherein, the ring gear component of said first compound planet gear for good and all is connected on the sun gear parts of said second compound planet gear, and the sun gear parts of said first compound planet gear for good and all are connected on the sun gear parts of said fourth line star gear cluster; The ring gear component of said the third line star gear cluster for good and all is connected on the planet carrier parts of said fourth line star gear cluster; Said gearbox output parts for good and all link with the planet carrier parts of said second compound planet gear and said the third line star gear cluster, and said gear box input parts for good and all link with the planet carrier parts of said first compound planet gear, and
Wherein, said transmission case have inwardly be defined as from the neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the first area defined by said first wall and said first compound planet gear, inwardly be defined as from the said neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the second area that defines by said first compound planet gear and said fourth line star gear cluster, inwardly be defined as from the said neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the 3rd zone defined by said fourth line star gear cluster and said the third line star gear cluster, inwardly be defined as from the said neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the 4th zone defined by said second compound planet gear and said the third line star gear cluster, inwardly be defined as from the said neighboring of said compound planet gear radially and from the 5th zone that the vertical line aimed at said gear box input component axial radially outwards and is axially upward defined by said second compound planet gear and said second wall and be defined as from said the 3rd wall radially inside and from the said neighboring of said compound planet gear radially outside and axial the 6th zone of upward defining by said first wall and said second wall;
First clutch, it is arranged in one of them zone in said first area, said second area, said the 3rd zone and said the 6th zone;
Second clutch, it is arranged in one of them zone in said first area, said second area, said the 3rd zone and said the 6th zone;
Three-clutch, it is arranged in one of them zone in said the 4th zone, said the 5th zone and said the 6th zone;
First drg, it is arranged in one of them zone in said first area, said second area, said the 5th zone and said the 6th zone;
Second drg, it is arranged in one of them zone in said first area, said second area, said the 5th zone and said the 6th zone; And
Wherein, Said first clutch, said second clutch, said three-clutch, said first drg and said second drg can engage selectively; Thereby between said gear box input parts and said gearbox output parts, set up at least eight speed of advances than with at least one reverse speed ratio and
Power transfer assemblies; It has first transmission gear and second transmission gear and power transmission component; Wherein, said first transmission gear rotatably is fixed on the said driving engine output block, and said second transmission gear rotatably is fixed on the said gear box input parts; And; Wherein, said power transmission component rotatably links up said first transmission gear and said second transmission gear, is used for rotation energy is sent to said second transmission gear from said first transmission gear;
The main reduction gear compound planet gear, it has main reduction gear first parts that are connected on the said gearbox output parts, is connected in main reduction gear second parts on the said transmission case, and main reduction gear the 3rd parts; With
Differential gear set; It has the differential gear box that is connected on said main reduction gear the 3rd parts; And has an a pair of gear that rotatably is supported in the said differential gear box; Wherein, said this rotatably is fixed on one of them of pair of wheels one of them of gear, and said this in the gear another rotatably be fixed on said this in the wheel another.
2. transaxle according to claim 1; It is characterized in that; Said first clutch can engage selectively, so that the sun gear component interconnect of wherein at least one and said the third line star gear cluster of the sun gear parts of the ring gear component of said first compound planet gear and said second compound planet gear is got up, and is arranged in the said first area; Said second clutch is arranged in the said first area; Said three-clutch is arranged in said the 4th zone, and said first drg is arranged in said the 6th zone, and said second drg is arranged in said the 6th zone.
3. transaxle according to claim 1 is characterized in that said first clutch is arranged in the said second area.
4. transaxle according to claim 1 is characterized in that, said first clutch is arranged in said the 3rd zone.
5. transaxle according to claim 1 is characterized in that, said first clutch is arranged in said the 6th zone.
6. transaxle according to claim 1; It is characterized in that; Said second clutch can engage selectively, so that the planet carrier parts of said first compound planet gear and the sun gear component interconnect of said the third line star gear cluster are got up, and; Wherein, said second clutch is arranged in the said first area.
7. transaxle according to claim 1 is characterized in that said second clutch is arranged in the said second area.
8. transaxle according to claim 1 is characterized in that, said second clutch is arranged in said the 3rd zone.
9. transaxle according to claim 1 is characterized in that, said second clutch is arranged in said the 6th zone.
10. transaxle according to claim 1; It is characterized in that; Said three-clutch can engage selectively, so that the ring gear component of said second compound planet gear and the sun gear component interconnect of said the third line star gear cluster are got up, and; Wherein, said three-clutch is arranged in said the 4th zone.
11. transaxle according to claim 1 is characterized in that, said three-clutch is arranged in said the 5th zone.
12. transaxle according to claim 1 is characterized in that, said three-clutch is arranged in said the 6th zone.
13. transaxle according to claim 1; It is characterized in that; Said first drg can engage selectively, so as with the sun gear component interconnect of the sun gear parts of said first compound planet gear and said fourth line star gear cluster on said transmission case, and; Wherein, said first drg is arranged in said the 6th zone.
14. transaxle according to claim 1 is characterized in that, said first drg is arranged in said the 5th zone.
15. transaxle according to claim 1 is characterized in that, said first drg is arranged in the said second area.
16. transaxle according to claim 1 is characterized in that, said first drg is arranged in the said first area.
17. transaxle according to claim 1 is characterized in that, said second drg can engage selectively; So that the ring gear component of said fourth line star gear cluster is interconnected on the said transmission case; And wherein, said second drg is arranged in said the 6th zone.
18. transaxle according to claim 1 is characterized in that, said second drg is arranged in said the 5th zone.
19. transaxle according to claim 1 is characterized in that, said second drg is arranged in the said second area.
20. transaxle according to claim 1 is characterized in that, said second drg is arranged in the said first area.
21. a transaxle that is connected on the driving engine output block, said transaxle comprises:
The gear box input parts;
The gearbox output parts;
Transmission case, the 3rd wall that it has first wall, second wall and between said first wall and said second wall, extends;
Be arranged on first compound planet gear, second compound planet gear, the third line star gear cluster and fourth line star gear cluster in the said transmission case; Wherein said first compound planet gear is adjacent to said first wall; Said second compound planet gear is adjacent to second wall; Said fourth line star gear cluster is adjacent to said first compound planet gear; And said the third line star gear cluster is between said fourth line star gear cluster and said second compound planet gear; Each said compound planet gear has sun gear parts, ring gear component and supports a plurality of planetary planet carrier parts; Said a plurality of planetary wheel respectively is configured to be meshing with each other with said sun gear parts and said ring gear component, and, wherein; The ring gear component of said first compound planet gear for good and all is connected on the sun gear parts of said second compound planet gear; The sun gear parts of said first compound planet gear for good and all are connected on the sun gear parts of said fourth line star gear cluster, and the ring gear component of said the third line star gear cluster for good and all is connected on the planet carrier parts of said fourth line star gear cluster, and said gearbox output parts for good and all link with the planet carrier parts of said second compound planet gear and said the third line star gear cluster; And said gear box input parts for good and all link with the planet carrier parts of said first compound planet gear, and
Wherein, said transmission case have inwardly be defined as from the neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the first area defined by said first wall and said first compound planet gear, inwardly be defined as from the said neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the second area that defines by said first compound planet gear and said fourth line star gear cluster, inwardly be defined as from the said neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the 3rd zone defined by said fourth line star gear cluster and said the third line star gear cluster, inwardly be defined as from the said neighboring of said compound planet gear radially and from the vertical line of aiming at said gear box input component axial radially outwards and axially go up the 4th zone defined by said second compound planet gear and said the third line star gear cluster, inwardly be defined as from the said neighboring of said compound planet gear radially and from the 5th zone that the vertical line aimed at said gear box input component axial radially outwards and is axially upward defined by said second compound planet gear and said second wall and be defined as from said the 3rd wall radially inside and from the said neighboring of said compound planet gear radially outside and axial the 6th zone of upward defining by said first wall and said second wall;
First clutch; It is arranged in one of them zone in said first area, said second area, said the 3rd zone and said the 6th zone; And can engage selectively, so that the ring gear component of said first compound planet gear and the sun gear component interconnect of said the third line star gear cluster are got up;
Second clutch; It is arranged in one of them zone in said first area, said second area, said the 3rd zone and said the 6th zone; And can engage selectively, so that the planet carrier parts of said first compound planet gear and the sun gear component interconnect of said the third line star gear cluster are got up;
Three-clutch; It is arranged in one of them zone in said the 4th zone, said the 5th zone and said the 6th zone; And can engage selectively, so that the ring gear component of said second compound planet gear and the sun gear component interconnect of said the third line star gear cluster are got up;
First drg; It is arranged in one of them zone in said first area, said second area, said the 5th zone and said the 6th zone; And can engage selectively, so as with the sun gear component interconnect of the sun gear parts of said first compound planet gear and said fourth line star gear cluster on said transmission case;
Second drg; It is arranged in one of them zone in said first area, said second area, said the 5th zone and said the 6th zone; And can engage selectively, so that the ring gear component of said fourth line star gear cluster is interconnected on the said transmission case; And
Wherein said first clutch, said second clutch, said three-clutch, said first drg and said second drg can engage selectively; Thereby between said gear box input parts and said gearbox output parts, set up at least eight speed of advances than with at least one reverse speed ratio and
Power transfer assemblies; It has first transmission gear and second transmission gear and power transmission component; Wherein, said first transmission gear rotatably is fixed on the said driving engine output block, and said second transmission gear rotatably is fixed on the said gear box input parts; And; Wherein, said power transmission component rotatably links up said first transmission gear and said second transmission gear, is used for rotation energy is sent to said second transmission gear from said first transmission gear;
The main reduction gear compound planet gear; It has the main reduction gear sun gear that is connected on the said gearbox output parts, is connected in the main reduction gear Ring gear on the said transmission case; And main reduction gear carriage member; It is rotatably supporting a plurality of miniature gearss of main reduction gear, said a plurality of miniature gearss and said main reduction gear sun gear and said main reduction gear Ring gear all be meshing with each other and
Differential gear set; It has the differential gear box that is connected on the said main reduction gear carriage member; And has an a pair of gear that rotatably is supported in the said differential gear box; Wherein, said this rotatably is fixed on one of them of pair of wheels one of them of gear, and said this in the gear another rotatably be fixed on said this in the wheel another.
22. transaxle according to claim 21 is characterized in that, said power transmission component is chain or band.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US3026108P | 2008-02-21 | 2008-02-21 | |
| US61/030261 | 2008-02-21 | ||
| US12/325,634 US8187138B2 (en) | 2008-02-21 | 2008-12-01 | Multi-speed transaxle for a front wheel drive vehicle |
| US12/325634 | 2008-12-01 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101513834A CN101513834A (en) | 2009-08-26 |
| CN101513834B true CN101513834B (en) | 2012-05-23 |
Family
ID=40998901
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100080679A Expired - Fee Related CN101513834B (en) | 2008-02-21 | 2009-02-20 | Multi-speed transaxle for a front wheel drive vehicle |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US8187138B2 (en) |
| CN (1) | CN101513834B (en) |
| DE (1) | DE102009009513B4 (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8197378B2 (en) * | 2008-02-20 | 2012-06-12 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8123652B2 (en) * | 2008-02-20 | 2012-02-28 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8118700B2 (en) * | 2008-02-20 | 2012-02-21 | GM Global Technology Operations LLC | Multi-speed transmission for a front wheel drive vehicle |
| US8187138B2 (en) * | 2008-02-21 | 2012-05-29 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8157696B2 (en) * | 2008-02-21 | 2012-04-17 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8075441B2 (en) * | 2008-03-31 | 2011-12-13 | GM Global Technology Operations LLC | Automatic transmission gear and clutch arrangement |
| US8267832B2 (en) * | 2008-04-16 | 2012-09-18 | GM Global Technology Operations LLC | Multi-speed transaxle |
| US8177676B2 (en) * | 2008-04-16 | 2012-05-15 | GM Global Technology Operations LLC | Multi-speed transaxle |
| US8192320B2 (en) * | 2008-04-18 | 2012-06-05 | GM Global Technology Operations LLC | Multi-speed transaxle |
| US8167767B2 (en) * | 2008-04-18 | 2012-05-01 | GM Global Technology Operations LLC | Multi-speed transaxle |
| US8047952B2 (en) * | 2008-04-21 | 2011-11-01 | GM Global Technology Operations LLC | Multi-speed transaxle |
| US8241167B2 (en) * | 2008-04-21 | 2012-08-14 | GM Global Technology Operations LLC | Multi-speed transaxle |
| US9618087B2 (en) | 2012-06-14 | 2017-04-11 | GM Global Technology Operations LLC | Automatic transmission gear and clutch arrangement |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19828184A1 (en) * | 1997-10-08 | 1999-04-15 | Hyundai Motor Co Ltd | Automotive five-speed automatic gearbox has transmission control unit |
| DE102005032880A1 (en) * | 2005-07-14 | 2007-02-01 | Zf Friedrichshafen Ag | Multi-stage, automatic epicyclic gearbox for vehicles, includes nine driven shafts and six change components providing nine forward and one reverse ratio |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4108777B2 (en) * | 1996-12-04 | 2008-06-25 | Ｇｋｎ ドライブライン トルクテクノロジー株式会社 | Power transmission device |
| US6106428A (en) * | 1998-03-23 | 2000-08-22 | Ford Global Technologies, Inc. | Compact dual mode continually variable transmission |
| DE202006006000U1 (en) | 2006-04-06 | 2006-06-14 | Zf Friedrichshafen Ag | Automatic gearbox design for vehicle, includes epicyclic gears, clutches and brakes providing eight forward gears and one reverse |
| DE202006006003U1 (en) | 2006-04-06 | 2006-06-22 | Zf Friedrichshafen Ag | Multi-stage transmission unit for vehicle, comprising three of five gear switch elements engaged with every gear selected |
| US7488268B2 (en) * | 2006-11-29 | 2009-02-10 | Gm Global Technology Operations, Inc. | Multi-speed transmission |
| US7699741B2 (en) * | 2007-01-25 | 2010-04-20 | Gm Global Technology Operations, Inc. | Multi-speed transmission |
| US7775931B2 (en) * | 2007-03-16 | 2010-08-17 | Gm Global Technology Operations, Inc. | Multi-speed transmission |
| US8123650B2 (en) * | 2008-02-20 | 2012-02-28 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8123651B2 (en) * | 2008-02-20 | 2012-02-28 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8118700B2 (en) * | 2008-02-20 | 2012-02-21 | GM Global Technology Operations LLC | Multi-speed transmission for a front wheel drive vehicle |
| US8123652B2 (en) * | 2008-02-20 | 2012-02-28 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8197378B2 (en) * | 2008-02-20 | 2012-06-12 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8187138B2 (en) * | 2008-02-21 | 2012-05-29 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8157696B2 (en) * | 2008-02-21 | 2012-04-17 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US7998015B2 (en) * | 2008-04-17 | 2011-08-16 | GM Global Technology Operations LLC | Multi-speed transaxle for a front wheel drive vehicle |
| US8292767B2 (en) * | 2008-06-04 | 2012-10-23 | GM Global Technology Operations LLC | Powertrain having a multi-speed transmission |
-
2008
- 2008-12-01 US US12/325,634 patent/US8187138B2/en not_active Expired - Fee Related
-
2009
- 2009-02-18 DE DE102009009513.6A patent/DE102009009513B4/en not_active Expired - Fee Related
- 2009-02-20 CN CN2009100080679A patent/CN101513834B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19828184A1 (en) * | 1997-10-08 | 1999-04-15 | Hyundai Motor Co Ltd | Automotive five-speed automatic gearbox has transmission control unit |
| DE102005032880A1 (en) * | 2005-07-14 | 2007-02-01 | Zf Friedrichshafen Ag | Multi-stage, automatic epicyclic gearbox for vehicles, includes nine driven shafts and six change components providing nine forward and one reverse ratio |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101513834A (en) | 2009-08-26 |
| US20090215581A1 (en) | 2009-08-27 |
| US8187138B2 (en) | 2012-05-29 |
| DE102009009513A1 (en) | 2009-10-15 |
| DE102009009513B4 (en) | 2018-07-26 |
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